US7484452B2 - Fluid end for a plunger pump - Google Patents
Fluid end for a plunger pump Download PDFInfo
- Publication number
- US7484452B2 US7484452B2 US11/142,852 US14285205A US7484452B2 US 7484452 B2 US7484452 B2 US 7484452B2 US 14285205 A US14285205 A US 14285205A US 7484452 B2 US7484452 B2 US 7484452B2
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- Prior art keywords
- tension member
- fluid end
- cylinder bore
- compressive load
- region
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
Definitions
- the present invention relates in general to pumps and more specifically to the fluid end of plunger pumps.
- High-pressure, reciprocating, plunger pumps have been used for many years and are a mainstay in the well services industry. These well service pumps often produce pressurized fluid in excess of 15,000 pounds per square inch. High stresses on the fluid ends of these pumps are associated with these high pressures.
- the present invention relates to reciprocating pumps.
- a fluid end for a reciprocating pump including a body having a base, a side and a longitudinal opposing side, a cylinder bore formed horizontally through the body and a vertical bore intersecting the cylinder bore defining a high stress region proximate the intersection, and a tension member extending through the body substantially parallel to the longitudinal axis of the body, wherein the tension member provides a compressive load on the body reducing the tensile stresses encountered in the region during operation of the fluid end.
- FIG. 1 is a perspective view of a prior art reciprocating pump
- FIG. 2 is a perspective view of an embodiment of the reciprocating pump of the present invention
- FIG. 3 is a front view of the fluid end of the present invention.
- FIG. 4 is a cross-sectional view of the fluid end of the present invention shown along the line 4 - 4 of FIG. 3 ;
- FIG. 5 is a side view of the fluid end of the present invention.
- FIG. 6 is a cross-sectional view of the fluid end of the present invention shown along the line 6 - 6 of FIG. 5 ;
- FIG. 7 is a partial cross-sectional view of the fluid end of the present invention illustrating the tensile (hoop) stresses encountered during operation and the reactive compressive loads provided;
- FIG. 8 is a graphical representation of an example of the stress reduction produced by the present invention.
- FIG. 1 is a perspective view of a prior art reciprocating plunger pump of the present invention, generally denoted by the numeral 1 .
- Pump 1 is a typical, high-pressure, reciprocating fluid pump. Pump one comprises three primary portions, a power end 12 , fluid end 3 and gear works 16 .
- the power end 12 is conventional and contains a crankshaft, connecting rods, and various machinery required to reciprocate a plunger within the bore and cylinder of fluid end 14 .
- the fluid end includes a suction intake manifold 18 and discharge ports 20 .
- the prior art fluid end 3 is susceptible to fatigue stresses that result in failure of pump 1 requiring expensive repairs and more often replacement.
- Prior techniques have been utilized with limited success to limit these fatigue failures. Such techniques include “autofrettage,” which has shown limited results.
- autofrettage is a laborious task and requires excessive pressure producing equipment.
- the minimum autofrettage pressure required to show any increase in fatigue life improvement is at least two times the pressure that results in yielding of the material. For example, an ideal autofrettage pressure is roughly 75,000 to 100,000 pounds per square inch.
- FIG. 2 is a perspective view of a reciprocating plunger pump, generally denoted by the numeral 10 , of the present invention.
- Pump 10 includes gear works 16 , power end 12 , and a internal material stress reducing fluid end 14 .
- Fluid end 14 includes tension members 22 extending through body 24 substantially parallel to the longitudinal axis of body 24 .
- FIG. 3 is a front view of fluid end 14 of the present invention in isolation.
- Fluid end 14 includes a body 24 .
- Cylinder heads 26 show that the illustrated fluid end 14 is for a triplex pump.
- FIG. 4 is a cross-section view of fluid end 14 shown along the line 4 - 4 of FIG. 3 .
- Body 24 forms a horizontal cylinder 28 having a bore 30 .
- Cylinder 28 and bore 30 connect to power end 12 ( FIG. 1 ) at connection 32 .
- cylinder 30 is adapted to carry the pump plunger.
- Body 24 also forms a vertical bore 34 that intersects cylinder bore 30 .
- This intersecting vertical and horizontal bore configuration is desired in the industry because of its compact profile. However, these intersecting bore configurations result in excessive failures by fatigue cracks that are produced at the high stress regions 36 proximate the intersection of horizontal bore 28 and vertical bore 34 .
- Tension members 22 are elongated members of sufficient strength to provide the compressive loads necessary to compress, or squeeze, the high stressed regions 36 .
- the present invention facilitates applying compressive stress at the high stressed regions 36 and the compressive stress thereby counters the tensile stresses in region 36 .
- the reduction in the tensile, hoop, stresses lengthens the service life of body 24 by the corresponding reduction of the tensile (hoop) stresses.
- Use of tension members 22 negates the need for the autofrettage process.
- FIG. 6 is a cross-sectional view of fluid end 14 of the present invention shown along the line 6 - 6 of FIG. 5 .
- longitudinal paths 38 are formed through body 24 substantially parallel to the longitudinal axis of body 24 . Paths 38 may be formed by drilling.
- a pair of longitudinal bores 38 may be formed proximate the base 40 of body 24 straddling vertical bore 34 .
- Longitudinal tension members 22 comprise a first end 42 and a second end 44 .
- first end 42 is a bolt head and second end 44 is threaded for mating with a nut 46 .
- tension members 22 may be elongated members wherein first and second ends 42 , 44 are both threaded and tension members 22 are compressively connected to body 24 via nuts 46 . It should be recognized that tension member 22 and the mechanisms for connecting and providing a compressive load via tension members 22 may be utilized without departing from the scope and spirit of the present invention.
- FIG. 7 is a partial cross-sectional view of fluid end 14 of the present invention.
- the tensile (hoop) stresses encountered in the high stress region 36 are illustrated by the circular arrows denoted by the numeral 70 .
- Stresses 70 are countered by the compressive load, illustrated by the arrows denoted by the numeral 72 , provided by tension members 22 .
- tension member path 38 and tension members 22 are positioned proximate high stress region 36 .
- Fluid head 14 is manufactured with paths 44 or retrofitted by forming paths 44 longitudinally through body 24 .
- a desirable number of two paths 44 may be formed.
- Tension members 22 are disposed in paths 44 so that first end 42 abuts an end 48 of body 24 , and the second end 44 extends beyond the opposing side 50 of body 24 .
- Nut 46 is threaded on second end 44 and threaded against opposing side 50 until a desired compressive load 72 is achieved at regions 36 .
- a desired compressive load 72 is used to counter the tensile (hoop) stresses 70 during operation of body 24 .
- tension members 22 may be adjusted to maintain a desired compressive load and/or be replaced.
- the tension members 22 and method of the present invention reduce the stress at regions 36 prolonging the life of the fluid end 14 .
- FIG. 8 is a graphical representation of an example of the reduction in stress encountered in pounds per square inch at region 36 ( FIG. 4 ) of the prior art fluid end 3 of FIG. 1 versus fluid end 14 of the present invention shown in FIGS. 2-6 .
- Curve 60 shows the stress at region 36 in fluid end 3 during operation of pump 1 .
- Curve 62 is the average stress encountered at region 36 of fluid end 3 during the operation of pump 1 .
- Curve 64 shows the stress at region 36 in fluid end 14 during the operation of pump 10 of the present invention.
- Curve 66 is the average stress encountered at region 36 of fluid end 14 during the operation of pump 10 of the present invention.
- the tension members and method of the present invention significantly reduce the stress encountered by body 24 of fluid end 14 . Thereby decreasing the occurrence of fatigue failure of the fluid end and reducing expensive repairs and replacement of fluid ends.
- the present invention additionally provides an effective and cost efficient means for addressing the disadvantages of the popular intersecting bore fluid end.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims (24)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/142,852 US7484452B2 (en) | 2004-07-01 | 2005-06-01 | Fluid end for a plunger pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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US58488904P | 2004-07-01 | 2004-07-01 | |
US11/142,852 US7484452B2 (en) | 2004-07-01 | 2005-06-01 | Fluid end for a plunger pump |
Publications (2)
Publication Number | Publication Date |
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US20060002806A1 US20060002806A1 (en) | 2006-01-05 |
US7484452B2 true US7484452B2 (en) | 2009-02-03 |
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US11/142,852 Active 2027-05-25 US7484452B2 (en) | 2004-07-01 | 2005-06-01 | Fluid end for a plunger pump |
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Cited By (28)
Publication number | Priority date | Publication date | Assignee | Title |
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US20080000065A1 (en) * | 2006-06-23 | 2008-01-03 | Partha Ganguly | Autofrettage process for a pump fluid end |
US20110081268A1 (en) * | 2009-08-13 | 2011-04-07 | Brian Ochoa | Pump body |
US20110255993A1 (en) * | 2010-02-26 | 2011-10-20 | Brian Ochoa | Precompression effect in pump body |
US20120063936A1 (en) * | 2010-09-10 | 2012-03-15 | Phoinix Global LLC | Modular fluid end for a multiplex plunger pump |
US20120148430A1 (en) * | 2009-08-13 | 2012-06-14 | Joe Hubenschmidt | Pump assembly |
US20120247578A1 (en) * | 2011-03-31 | 2012-10-04 | Halliburton Energy Services, Inc. | Pump Manifold Support |
US20130014640A1 (en) * | 2011-07-12 | 2013-01-17 | Frac Tech Services, Llc | Laser peened fluid end for a high pressure pump |
US20130042752A1 (en) * | 2009-09-03 | 2013-02-21 | William Marshall | Pump Body |
WO2013116535A1 (en) * | 2012-02-01 | 2013-08-08 | S.P.M. Flow Control, Inc. | Pump fluid end with integrated web portion |
CN103339379A (en) * | 2010-12-09 | 2013-10-02 | S.P.M.流量控制股份有限公司 | Offset valve bore for a reciprocating pump |
USD691180S1 (en) | 2012-04-27 | 2013-10-08 | S.P.M. Flow Control, Inc. | Center portion of a fluid cylinder for a pump |
US20130319220A1 (en) * | 2010-10-19 | 2013-12-05 | Schlumberger Technology Corporation | Fluid End Reinforced With Abrasive Resistant Insert, Coating Or Lining |
USD706397S1 (en) | 2011-08-19 | 2014-06-03 | S.P.M. Flow Control, Inc. | Portion of fluid end |
USD706832S1 (en) | 2012-06-15 | 2014-06-10 | S.P.M. Flow Control, Inc. | Fluid cylinder for a pump |
WO2015038248A1 (en) * | 2013-09-10 | 2015-03-19 | Serva Group Llc | Housing for high-pressure fluid applications |
US9341179B2 (en) | 2010-02-26 | 2016-05-17 | Schlumberger Technology Corporation | Precompression effect in pump body |
US9383015B2 (en) | 2013-05-21 | 2016-07-05 | Gardner Denver, Inc. | Fluid end having spherical cross-bore intersection |
US9528508B2 (en) | 2009-09-03 | 2016-12-27 | Schlumberger Technology Corporation | Pump assembly |
US9739130B2 (en) | 2013-03-15 | 2017-08-22 | Acme Industries, Inc. | Fluid end with protected flow passages |
EP3146210A4 (en) * | 2014-05-23 | 2018-01-17 | FMC Technologies, Inc. | Reciprocating pump with improved fluid cylinder cross-bore geometry |
US20180156212A1 (en) * | 2016-11-22 | 2018-06-07 | American Manufacturing Innovators, Inc. | Packing bore for eliminating washout failure |
US20190101109A1 (en) * | 2017-10-02 | 2019-04-04 | S.P.M. Flow Control, Inc. | Valve stop |
US10337508B2 (en) | 2016-06-17 | 2019-07-02 | Gardner Denver Petroleum Pumps, Llc | Fluid-end of a high pressure pump |
US10378538B2 (en) * | 2012-11-16 | 2019-08-13 | George H Blume | Fluid end and center feed suction manifold |
US10794381B2 (en) | 2017-04-26 | 2020-10-06 | Gardner Denver Petroleum Pumps, Llc | Reciprocating pump with improved cross-bore |
US10995738B2 (en) * | 2019-07-08 | 2021-05-04 | George H. Blume | Fluid end and center feed suction manifold |
US20230018160A1 (en) * | 2015-09-29 | 2023-01-19 | Kerr Machine Co. | Sealing high pressure flow devices |
US20230021141A1 (en) * | 2015-09-29 | 2023-01-19 | Kerr Machine Co. | Sealing high pressure flow devices |
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US20110189040A1 (en) * | 2010-01-29 | 2011-08-04 | Vicars Berton L | Fluid end |
US8998593B2 (en) * | 2010-02-24 | 2015-04-07 | J-Mac Tool, Inc. | Fluid end assembly |
US9322402B2 (en) | 2010-02-24 | 2016-04-26 | J-Mac Tool, Inc. | Dove-tail clamp |
USD705817S1 (en) | 2012-06-21 | 2014-05-27 | S.P.M. Flow Control, Inc. | Center portion of a fluid cylinder for a pump |
US11486502B2 (en) | 2015-09-29 | 2022-11-01 | Kerr Machine Co. | Sealing high pressure flow devices |
US10670013B2 (en) | 2017-07-14 | 2020-06-02 | Kerr Machine Co. | Fluid end assembly |
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US10760569B2 (en) | 2017-05-24 | 2020-09-01 | John L. Strelow | Reciprocating pumps and closures therefore |
US10962001B2 (en) | 2017-07-14 | 2021-03-30 | Kerr Machine Co. | Fluid end assembly |
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US11708830B2 (en) * | 2017-12-11 | 2023-07-25 | Kerr Machine Co. | Multi-piece fluid end |
US11788527B2 (en) * | 2018-12-10 | 2023-10-17 | Kerr Machine Co. | Fluid end |
USD916240S1 (en) | 2018-12-10 | 2021-04-13 | Kerr Machine Co. | Fluid end |
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US11578710B2 (en) | 2019-05-02 | 2023-02-14 | Kerr Machine Co. | Fracturing pump with in-line fluid end |
US11294402B1 (en) | 2019-07-01 | 2022-04-05 | CS&P Technologies LP | Segmented fluid end assembly |
US20220397107A1 (en) | 2019-11-18 | 2022-12-15 | Kerr Machine Co. | Fluid end assembly |
US11644018B2 (en) | 2019-11-18 | 2023-05-09 | Kerr Machine Co. | Fluid end |
US11686296B2 (en) | 2019-11-18 | 2023-06-27 | Kerr Machine Co. | Fluid routing plug |
US20220389916A1 (en) | 2019-11-18 | 2022-12-08 | Kerr Machine Co. | High pressure pump |
US11578711B2 (en) | 2019-11-18 | 2023-02-14 | Kerr Machine Co. | Fluid routing plug |
US11635068B2 (en) | 2019-11-18 | 2023-04-25 | Kerr Machine Co. | Modular power end |
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Cited By (51)
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US20080000065A1 (en) * | 2006-06-23 | 2008-01-03 | Partha Ganguly | Autofrettage process for a pump fluid end |
US9249798B2 (en) * | 2006-06-23 | 2016-02-02 | Schlumberger Technology Corporation | Autofrettage process for a pump fluid end |
US20110081268A1 (en) * | 2009-08-13 | 2011-04-07 | Brian Ochoa | Pump body |
US20120148430A1 (en) * | 2009-08-13 | 2012-06-14 | Joe Hubenschmidt | Pump assembly |
US8601687B2 (en) | 2009-08-13 | 2013-12-10 | Schlumberger Technology Corporation | Pump body |
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US9121402B2 (en) * | 2009-09-03 | 2015-09-01 | Schlumberger Technology Corporation | Pump body |
US9528508B2 (en) | 2009-09-03 | 2016-12-27 | Schlumberger Technology Corporation | Pump assembly |
US20130042752A1 (en) * | 2009-09-03 | 2013-02-21 | William Marshall | Pump Body |
US20110255993A1 (en) * | 2010-02-26 | 2011-10-20 | Brian Ochoa | Precompression effect in pump body |
US9341179B2 (en) | 2010-02-26 | 2016-05-17 | Schlumberger Technology Corporation | Precompression effect in pump body |
US20120063936A1 (en) * | 2010-09-10 | 2012-03-15 | Phoinix Global LLC | Modular fluid end for a multiplex plunger pump |
US8465268B2 (en) * | 2010-09-10 | 2013-06-18 | Phoinix Global LLC | Compression clamp for a modular fluid end for a multiplex plunger pump |
US9791082B2 (en) | 2010-09-10 | 2017-10-17 | Forum Us, Inc. | Modular fluid end for a multiplex plunger pump |
US20130319220A1 (en) * | 2010-10-19 | 2013-12-05 | Schlumberger Technology Corporation | Fluid End Reinforced With Abrasive Resistant Insert, Coating Or Lining |
CN103339379A (en) * | 2010-12-09 | 2013-10-02 | S.P.M.流量控制股份有限公司 | Offset valve bore for a reciprocating pump |
US8668470B2 (en) | 2010-12-09 | 2014-03-11 | S.P.M. Flow Control, Inc. | Offset valve bore for a reciprocating pump |
US9784262B2 (en) | 2010-12-09 | 2017-10-10 | S.P.M. Flow Control, Inc. | Offset valve bore in a reciprocating pump |
US9989044B2 (en) | 2010-12-09 | 2018-06-05 | S.P.M. Flow Control, Inc. | Offset valve bore in a reciprocating pump |
US8662865B2 (en) | 2010-12-09 | 2014-03-04 | S.P.M. Flow Control, Inc. | Offset valve bore in a reciprocating pump |
US8662864B2 (en) | 2010-12-09 | 2014-03-04 | S.P.M. Flow Control, Inc. | Offset valve bore in a reciprocating pump |
US8444398B2 (en) * | 2011-03-31 | 2013-05-21 | Halliburton Energy Services, Inc. | Pump manifold support |
US20120247578A1 (en) * | 2011-03-31 | 2012-10-04 | Halliburton Energy Services, Inc. | Pump Manifold Support |
US20130014640A1 (en) * | 2011-07-12 | 2013-01-17 | Frac Tech Services, Llc | Laser peened fluid end for a high pressure pump |
USD706397S1 (en) | 2011-08-19 | 2014-06-03 | S.P.M. Flow Control, Inc. | Portion of fluid end |
US11401930B2 (en) | 2012-01-27 | 2022-08-02 | Spm Oil & Gas Inc. | Method of manufacturing a fluid end block with integrated web portion |
US9945362B2 (en) | 2012-01-27 | 2018-04-17 | S.P.M. Flow Control, Inc. | Pump fluid end with integrated web portion |
US10330097B2 (en) | 2012-01-27 | 2019-06-25 | S.P.M. Flow Control, Inc. | Pump fluid end with integrated web portion |
WO2013116535A1 (en) * | 2012-02-01 | 2013-08-08 | S.P.M. Flow Control, Inc. | Pump fluid end with integrated web portion |
CN104204519A (en) * | 2012-02-01 | 2014-12-10 | S.P.M.流量控制股份有限公司 | Pump fluid end with integrated web portion |
USD691180S1 (en) | 2012-04-27 | 2013-10-08 | S.P.M. Flow Control, Inc. | Center portion of a fluid cylinder for a pump |
USD706833S1 (en) | 2012-04-27 | 2014-06-10 | S.P.M. Flow Control, Inc. | Center portion of a fluid cylinder for a pump |
USD706832S1 (en) | 2012-06-15 | 2014-06-10 | S.P.M. Flow Control, Inc. | Fluid cylinder for a pump |
US10378538B2 (en) * | 2012-11-16 | 2019-08-13 | George H Blume | Fluid end and center feed suction manifold |
US9739130B2 (en) | 2013-03-15 | 2017-08-22 | Acme Industries, Inc. | Fluid end with protected flow passages |
US9383015B2 (en) | 2013-05-21 | 2016-07-05 | Gardner Denver, Inc. | Fluid end having spherical cross-bore intersection |
US20160208797A1 (en) * | 2013-09-10 | 2016-07-21 | Serva Group ,LLC | Housing for hi-pressure fluid applications |
US9989053B2 (en) * | 2013-09-10 | 2018-06-05 | Serva Group Llc | Housing for high-pressure fluid applications |
WO2015038248A1 (en) * | 2013-09-10 | 2015-03-19 | Serva Group Llc | Housing for high-pressure fluid applications |
US10683862B2 (en) | 2013-09-10 | 2020-06-16 | Serva Group Llc | Housing for high-pressure fluid applications |
EP3146210A4 (en) * | 2014-05-23 | 2018-01-17 | FMC Technologies, Inc. | Reciprocating pump with improved fluid cylinder cross-bore geometry |
US11649901B2 (en) * | 2015-09-29 | 2023-05-16 | Kerr Machine Co. | Sealing high pressure flow devices |
US11649900B2 (en) * | 2015-09-29 | 2023-05-16 | Kerr Machine Co. | Sealing high pressure flow devices |
US20230021141A1 (en) * | 2015-09-29 | 2023-01-19 | Kerr Machine Co. | Sealing high pressure flow devices |
US20230018160A1 (en) * | 2015-09-29 | 2023-01-19 | Kerr Machine Co. | Sealing high pressure flow devices |
US10337508B2 (en) | 2016-06-17 | 2019-07-02 | Gardner Denver Petroleum Pumps, Llc | Fluid-end of a high pressure pump |
US10514031B2 (en) * | 2016-11-22 | 2019-12-24 | American Manufacturing Innovators, Inc. | Packaging bore for eliminating washout failure |
US20180156212A1 (en) * | 2016-11-22 | 2018-06-07 | American Manufacturing Innovators, Inc. | Packing bore for eliminating washout failure |
US10794381B2 (en) | 2017-04-26 | 2020-10-06 | Gardner Denver Petroleum Pumps, Llc | Reciprocating pump with improved cross-bore |
US20190101109A1 (en) * | 2017-10-02 | 2019-04-04 | S.P.M. Flow Control, Inc. | Valve stop |
US10995738B2 (en) * | 2019-07-08 | 2021-05-04 | George H. Blume | Fluid end and center feed suction manifold |
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US20060002806A1 (en) | 2006-01-05 |
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